US6532764B1 - Degree of supercooling control type expansion valve - Google Patents

Degree of supercooling control type expansion valve Download PDF

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Publication number
US6532764B1
US6532764B1 US09/390,152 US39015299A US6532764B1 US 6532764 B1 US6532764 B1 US 6532764B1 US 39015299 A US39015299 A US 39015299A US 6532764 B1 US6532764 B1 US 6532764B1
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United States
Prior art keywords
refrigerant
valve seat
force
exertion
valve
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
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US09/390,152
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English (en)
Inventor
Hisatoshi Hirota
Shinji Saeki
Tokumi Tsugawa
Yuusuke Inoue
Katsumi Koyama
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TGK Co Ltd
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TGK Co Ltd
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Assigned to TGK CO., LTD. reassignment TGK CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIROTA, HISATOSHI, INOUE, YUUSUKE, KOYAMA, KATSUMI, SAEKI, SHINJI, TSUGAWA, TOKUMI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/062—Capillary expansion valves

Definitions

  • the invention relates to a degree-of-supercooling control type expansion valve upstream of an evaporator in a refrigerating cycle and containing a valve seat, a valve body, a throttling portion and a force exerting means biasing said valve body towards said valve seat, according to the preamble part of claim 1 and to the preamble part of independent claim 2 .
  • a conventionally used expansion valve in a refrigerating cycle is a so-called temperature type expansion valve controlling the discharge of a refrigerant entering an evaporator in response to the temperature and the pressure of a low-pressure refrigerant discharge from the evaporator.
  • an expansion valve of a degree-of-supercooling control type can be used.
  • Said expansion valve is designed with a simple configuration and is able to constantly control the degree-of-supercooling of the high-pressure refrigerant. This allows to achieve a very simple, compact configuration of the valve and the refrigerating cycle.
  • said known expansion valve of the degree-of-supercooling control type has a drawback because the degree-of-supercooling cannot be adjusted finely when the valve is assembled, which degree-of-supercooling, however, must be kept constant, e.g. in a series of production of a identical valves of said type.
  • the above-mentioned object can be achieved by providing an exerting force adjusting member for finely adjusting the exerting force and by forming either the throttling portion or the valve seat structurally with the exerting force adjusting member.
  • Said exerting force adjusting member is provided such that it allows to adjust the exerting force either during assembly or even after assembly of the expansion valve in a series of such expansion valve having identical structural features. Said adjustment can be carried out in order to keep the degree-of-supercooling of a high-pressure refrigerant constant, e.g. among a series of identical expansion valves.
  • said exerting force adjusting member simultaneously is forming said valve seat, it does indirectly support said force exerting means via said valve body.
  • said throttling portion is formed with said valve body co-operating with said valve seat.
  • said exerting force adjusting member is carrying out a dual function, while in the second case even the valve body is carrying out a dual function.
  • valve seat formed with said exerting force adjusting member said counterfort is formed with said throttling portion. Also in this case, both components carry out dual function.
  • said counterfort is formed with said valve seat.
  • said counterfort and said force exerting adjusting member fulfil dual functions and allow to achieve a compact and structurally simple design.
  • both said exerting force adjusting member and said counterfort are formed with a respective valve seat and two opposed valve bodies are associated to both valve seats so that both valve bodies are biased in opposite directions by a common force exerting means and both valve bodies being formed with respective throttling portions.
  • both valve seats are located oppositely with a certain intermediate distance between them.
  • a controlled flow in both directions is possible, which might be desirable e.g. for a refrigerating cycle also used as a heating cycle. This design results in a bi-directional expansion valve.
  • check valves restricting the inflow of refrigerant from the external side into the expansion valve.
  • Structurally simple said check valves are integrated into the throttling portions wherein the throttle openings simultaneously constitute valve seats for the check valves.
  • Said force exerting means can be at least one spring.
  • said spring is made from a shape memorising alloy providing a temperature depending variable spring constant.
  • the spring is responsive to a temperature rise in the refrigerant by a spring constant increase. This leads to the positive effect that the degree-of-supercooling as controlled constantly increases when a load for the refrigerating cycle is large and consequently the temperature of the refrigerant starts to rise. Thereby, the cooling power increases permitting the adaptation of the cooling effect to the outside condition.
  • the force exerting adjusting member is threadably received in the refrigerant passage. This allows to gradually adjust the exerting force or to steplessly vary the pre-load of the force exerting means.
  • said exerting force adjusting member can be positioned by a press-fit in axial direction within the refrigerant passage in the proper position in order to adjust the exerting force to a desired value.
  • said throttling portion which conventionally is a through bore, instead may be shaped with an annular or ring-shaped cross-section. Having the same throttling factor across the throttling portion a ring-shaped throttling portion is providing an enlarged contact surface for the refrigerant leading to the positive effect of a greatly reduced passing sound of the refrigerant.
  • a ring-shaped throttling portion avoids the formation of an undesirable operation noise source.
  • Said ring-shaped cross-section can be formed by discrete ring segments or with a continuous ring shape.
  • FIG. 1A longitudinal section of an expansion valve of the degree-of-supercooling control type, corresponding to a first embodiment
  • FIG. 2A longitudinal section of a second embodiment
  • FIG. 3A longitudinal section of a third embodiment
  • FIG. 4A longitudinal section of a fourth embodiment
  • FIG. 5A illustrates a cross-sectional detail view of the embodiment of FIG. 4 in section plane denoted 5 A— 5 A;
  • FIG. 5B illustrates a cross-sectional detail view of the embodiment of FIG. 4 in section plane denoted 5 B— 5 B;
  • FIG. 6A longitudinal section of a fifth embodiment
  • FIG. 7A longitudinal section of a sixth embodiment
  • FIG. 8A longitudinal section of a seventh embodiment
  • FIG. 9A temperature/pressure characteristic diagram illustrating the degree-of-supercooling of the refrigerant by the expansion valve of at least one of the preceding embodiments.
  • FIG. 1 in the middle of a refrigerant line 1 of a refrigerating cycle of a cooling equipment for an automobile (not shown in detail) a stepped cylindrical body 2 is fixedly arranged. Said cylindrical body 2 is designed to allow that a high-pressure refrigerant flows from the upstream side (left) to the downstream side (right) and into a not shown evaporator.
  • a valve seat 4 is formed at the inlet side of cylindrical body 2 .
  • a valve body 5 is arranged oppositely to valve seat 4 in a state in which valve body 5 is exerted from the downstream side by the exciting force of a compression coil spring defining a force exerting means 6 .
  • valve body 5 With a balance between the pressure difference of the refrigerant pressure from the upstream side to the downstream side of valve seat 4 and the force of spring 6 , valve body 5 is separated from valve seat 4 in order to control the discharge of refrigerant passing the refrigerant line 1 .
  • Valve body 5 has a circular conical surface facing valve seat 4 and is loosely fitted to refrigerant passage hole 3 b by means of e.g. three foot pieces 5 b projecting from valve body 5 and entering refrigerant passage hole 3 b e.g. in order to guide valve body 5 during its movements in relation to valve seat 4 .
  • Valve seat 4 is shown as a conical valve seat.
  • At the downstream side of valve body 5 e.g. three foot pieces 5 a protrude from valve body 5 .
  • Foot pieces 5 a are arranged along the inner periphery of refrigerant passage hole 3 b, e.g. in order to also guide valve body 5 during its operational movement.
  • a refrigerant passage hole is drilled defining a throttling portion 8 for generating an adiabatic expansion to the passing refrigerant.
  • Said throttling portion 8 at least partially is formed very thin in order to define a flow restrictor.
  • a not shown evaporator is connected to the downstream side of the expansion valve. The refrigerant passing throttling portion 8 is sent to the evaporator while being subjected to an adiabatic expansion.
  • the high-pressure refrigerant at the upstream side of valve seat 4 is a liquid in supercooled state.
  • the refrigerant looses supercooling due to foams occurring within the liquid after passing through the operating nip between valve seat 4 and valve body 5 . Therefore, if the degree-of-supercooling of high-pressure refrigerant at the upstream side is lowered, the amount of foam in the refrigerant downstream of valve seat 4 is increasing, and, as a result, the discharge of refrigerant is decreasing as well, and the degree-of-supercooling of the refrigerant at the upstream side is increasing again.
  • the throttling portion 8 it might be advantageous to coat the throttling portion 8 with a material having good lubricity.
  • a suitable material might be ethylene tetrafluoride resin. Instead a part could be inserted into member 7 forming throttling portion 8 of such material. As a further alternative, member 7 entirely could be formed of such material. With the good lubricating effect of said material clogging of the throttling portion 8 due to sticking of sludge contained in the refrigerant can be prevented.
  • refrigerant passage hole 3 a and valve seat 4 both are formed by a narrowed section of a pipe 1 a of the refrigerant line 1 (pressing deformation of the pipe).
  • Exerting force adjusting member 7 in this embodiment is disk-shaped and is a press-in member pressed into pipe 1 a into a suitable axial position, e.g. during assembly of the expansion valve, and is fixed to the inner periphery of pipe 1 a.
  • the degree-of-supercooling finally can be adjusted depending on the axial position of member 7 by solely pressing member 7 into the right position. No threading work is required and a simpler, more compact configuration can be achieved.
  • exerting force adjusting member 7 ′ is in the form of a cylindrical member in which the refrigerant passage hole 3 a at the inlet side and valve seat 4 at the outlet side are integrally formed.
  • Member 10 is pressed in and fixed to the inner periphery of pipe 1 a of the refrigerant line 1 .
  • a disk-shaped member is axially fixed in its position, e.g. by caulking pipe 1 a , and with a certain axial distance from member 7 ′ which distance suffices to receive valve body 5 and spring 6 .
  • Member 7 ′ indirectly supports the force of spring 6 via valve body 5 .
  • Counterfort 10 is formed with throttling portion 8 in the form of a central through bore.
  • the degree-of-supercooling finely can be adjusted by selecting the position of member 7 ′ when pressing cylindrical member 7 ′ into the pipe section 1 a of the refrigerant line 1 , e.g. during assembly. A simple and compact design is achieved.
  • throttling portion 8 does not have the form of a centre bore but is made with a ring-shaped cross-section as shown in FIGS. 5A and 5B. With a ring-shape of the throttling portion 8 the passing sound of the refrigerant is very quiet compared to a throttling portion with the form of a round hole shape. A ring-shaped cross-section of the throttling portion 8 thus provides the advantage of causing no noise source.
  • Said throttling portion 8 might be formed with a continuous ring-shape as shown in FIG. 5B or can consist of a plurality of separated slots as shown in FIG. 5 A. Separated slots are provided in order to form member 7 ′ as one unitary body.
  • a continuous ring-shaped portion (corresponding to FIG. 5B) is located at the upstream side of the plurality of separated arcuate slots (corresponding to FIG. 5 A). This arrangement leads to the same effect as the form of the throttling portion 8 in FIG. 4 .
  • Valve seat 4 is formed by throttling the pipe 1 a itself of the refrigerant line 1 . Exerting force adjusting member 7 ′ (a cylindrical body) is pressed in and fixed into pipe 1 a . Member 7 ′ is formed with valve seat 4 ′ co-operating with the second valve body 5 ′. Both valve bodies 5 , 5 ′ are arranged oppositely with a certain axial interspace between them for co-operation with their associated to valve seats 4 , 4 ′. Between both valve bodies 5 , 5 ′ as force exerting means a compression coil spring 6 is provided so that both valve bodies 5 , 5 ′ are exerted towards their valve seats 4 , 4 ′. By adjusting the position of pressed in member 7 ′, e.g. during assembly, the magnitude of the discharge amount of the high-pressure refrigerant to be maintained constant can be finely adjusted.
  • valve body 5 at the upstream side of the flow of refrigerant performs the discharge control of the refrigerant and throttling portion 8 ′ formed in valve body 5 ′ at the downstream side is acting as the flow restrictor for adiabatic expansion of the refrigerant towards the evaporator.
  • the expansion valve of FIG. 7 is a so-called bi-directional expansion valve.
  • FIG. 8 is also a bi-directional expansion valve.
  • a check valve 11 is arranged blocking the flow from the outer side against the mouth of each throttling portion 8 , thereby restricting the inflow of refrigerant from the outside into each throttling portion 8 , 8 ′. Blocking throttling portion 8 at the upstream side avoids a leakage flow of refrigerant.
  • Both check valves 11 are operating automatically. They have a valve body co-operating with a valve seat defined by the mouth of the associated to throttling portion 8 , 8 ′. The valve bodies are guided by foot pieces 5 a. The position of press-in exerting force adjusting member 7 ′ determines the exerting force for both valve bodies 5 , 5 ′.
  • the degree-of-supercooling controlled constantly increases when a load for the refrigerating cycle is large and the temperature of the refrigerant is rising.
  • the degree-of-supercooling controlled constantly increases as the load becomes larger and the cooling power becomes larger thereby permitting to adapt the cooling to the outside conditions.
  • Forming either the throttling portion 8 , 8 ′ or valve seat 4 , 4 ′ with the exerting force adjusting member 7 , 7 ′ allows to achieve a very simple, compact configuration.
  • the exerting force adjusting member to set the exerting force by selectively varying the axial position of the member a fine adjustment can be performed easily when setting the degree-of-supercooling of the high-pressure refrigerant at the upstream side which should be maintained constant and should be controlled.
  • the force exerting means is constituted by a spring 6 move from a shape memorising alloy so that the spring constant of the spring increases in response to a temperature rise, the degree-of-supercooling can be controlled more constantly. If the load becomes larger, it can be made much higher to intensify the cooling power, thereby adapting the cooling power corresponding to the surrounding conditions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Temperature-Responsive Valves (AREA)
US09/390,152 1998-09-18 1999-09-03 Degree of supercooling control type expansion valve Expired - Fee Related US6532764B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP26485198 1998-09-18
JP10-264851 1998-09-18
JP11-019513 1999-01-28
JP01951399A JP3517369B2 (ja) 1998-09-18 1999-01-28 過冷却度制御式膨張弁

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US (1) US6532764B1 (fr)
EP (1) EP0987505B1 (fr)
JP (1) JP3517369B2 (fr)
DE (1) DE69924798T2 (fr)
ES (1) ES2241218T3 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050183439A1 (en) * 2004-02-23 2005-08-25 Alexander Lifson Fluid diode expansion device for heat pumps
US20090289207A1 (en) * 2008-03-27 2009-11-26 Fabian Mauricio Barreda Airflow regulating valve assembly
US20100257916A1 (en) * 2008-03-27 2010-10-14 Ip Innovative Products, Llc Accuracy enhancing valve assembly and related method of use
US20100263397A1 (en) * 2009-04-16 2010-10-21 Fujikoki Corporation Motor-operated valve and refrigeration cycle using the same
US20110154853A1 (en) * 2009-12-24 2011-06-30 Denso Corporation Decompression device
US8944098B1 (en) 2011-06-03 2015-02-03 Juan Carlos Bocos Airflow restricting valve assembly
CN105588380A (zh) * 2014-11-12 2016-05-18 株式会社鹭宫制作所 节流装置及具备该节流装置的冷冻循环系统
US20180202567A1 (en) * 2015-09-04 2018-07-19 Saginomiya Seisakusho, Inc. Throttling device and refrigeration cycle
US10222107B2 (en) 2015-06-03 2019-03-05 Saginomiya Seisakusho, Inc. Throttle device and refrigeration cycle system with same
US10731904B2 (en) 2015-12-02 2020-08-04 Mitsubishi Electric Corporation Air conditioner
US20230034413A1 (en) * 2021-07-29 2023-02-02 Beaconmedaes Llc High flow check valve for medical gas applications

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Publication number Priority date Publication date Assignee Title
JP2001004252A (ja) * 1999-06-24 2001-01-12 Tgk Co Ltd 過冷却度制御式膨張弁
JP3757784B2 (ja) 2000-04-06 2006-03-22 株式会社デンソー 減圧装置およびそれを用いた冷凍サイクル装置
JP3515048B2 (ja) 2000-06-21 2004-04-05 株式会社テージーケー 過冷却度制御式膨張弁
EP1508758A1 (fr) 2003-08-21 2005-02-23 A/S Dybvad Stalindustri Robinet
JP4352879B2 (ja) * 2003-11-28 2009-10-28 東海ゴム工業株式会社 バルブ内蔵コネクタ
JP2006275428A (ja) * 2005-03-29 2006-10-12 Tgk Co Ltd 温度差圧感知弁
JP2006292184A (ja) * 2005-04-06 2006-10-26 Tgk Co Ltd 膨張装置
JP5292537B2 (ja) * 2006-08-25 2013-09-18 株式会社テージーケー 膨張装置
WO2009060465A2 (fr) * 2007-07-18 2009-05-14 Vijay Appa Kasar Dispositif d'expansion économiseur d'énergie pour la réfrigération et autres branches d'industrie
DE102008005074A1 (de) * 2008-01-18 2009-07-23 Valeo Klimasysteme Gmbh Ejektor für eine Klimaanlage
JP5305860B2 (ja) * 2008-11-25 2013-10-02 三菱電機株式会社 膨張弁機構及びそれを搭載した空気調和装置
DE102010019327B4 (de) * 2010-05-03 2016-11-03 Kendrion (Villingen) Gmbh Ventileinrichtung
CN102235394B (zh) * 2011-08-15 2013-10-09 宁波广天赛克思液压有限公司 一种用于液压马达制动器控制的带油路选择的集成阀
JP6178281B2 (ja) * 2014-05-16 2017-08-09 株式会社鷺宮製作所 絞り装置、および、それを備える冷凍サイクルシステム
JP6178374B2 (ja) * 2014-11-12 2017-08-09 株式会社鷺宮製作所 絞り装置、および、それを備える冷凍サイクルシステム
WO2016194388A1 (fr) * 2015-06-03 2016-12-08 株式会社鷺宮製作所 Dispositif d'étranglement, et système à cycle de réfrigération le comprenant
CN106918170A (zh) * 2015-12-24 2017-07-04 吴亚妹 一种可卸荷节流阀装置
CN107191718B (zh) * 2017-04-21 2019-04-19 青岛海尔空调器有限总公司 用于空调器的针孔节流器的调试更换组件

Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1687209A (en) * 1927-04-09 1928-10-09 Tryco Products Inc Temperature and pressure relief valve
CH285258A (de) 1949-02-02 1952-08-31 Joergen Joergensen Hans Regelventil an Kälteanlagen.
US3387625A (en) * 1965-06-24 1968-06-11 W L Molding Company Check valve
US3805824A (en) 1972-09-25 1974-04-23 Us Navy Pressure-compensated flow control valve
US3943969A (en) * 1975-04-25 1976-03-16 Albert Rubin Positive acting check valve of polyvinylchloride to open in response to predetermined line pressure
US4066096A (en) 1975-07-25 1978-01-03 Aqueduct, Inc. Flow-control valve
JPS567959A (en) 1979-06-29 1981-01-27 Nippon Denso Co Refrigeration device
US4545405A (en) * 1983-11-09 1985-10-08 Thomas Industries, Inc. Multi-position relief valve
EP0255035A2 (fr) 1986-07-23 1988-02-03 Sanden Corporation Circuit frigorifique
US4932429A (en) * 1988-02-19 1990-06-12 Masatoshi Watanabe Screw stopper including anti-freeze device used for water pipe valve
US5004008A (en) 1990-04-02 1991-04-02 Carrier Corporation Variable area refrigerant expansion device
US5139047A (en) * 1991-09-27 1992-08-18 Marotta Scientific Controls, Inc. Miniature check valve construction
US5161572A (en) * 1989-11-13 1992-11-10 Robert Bosch Gmbh Pressure valve
US5170638A (en) * 1990-02-01 1992-12-15 Carrier Corporation Variable area refrigerant expansion device
US5332000A (en) * 1993-01-05 1994-07-26 Gassner, Inc. Low pressure sensitive valve

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1687209A (en) * 1927-04-09 1928-10-09 Tryco Products Inc Temperature and pressure relief valve
CH285258A (de) 1949-02-02 1952-08-31 Joergen Joergensen Hans Regelventil an Kälteanlagen.
US3387625A (en) * 1965-06-24 1968-06-11 W L Molding Company Check valve
US3805824A (en) 1972-09-25 1974-04-23 Us Navy Pressure-compensated flow control valve
US3943969A (en) * 1975-04-25 1976-03-16 Albert Rubin Positive acting check valve of polyvinylchloride to open in response to predetermined line pressure
US4066096A (en) 1975-07-25 1978-01-03 Aqueduct, Inc. Flow-control valve
JPS567959A (en) 1979-06-29 1981-01-27 Nippon Denso Co Refrigeration device
US4545405A (en) * 1983-11-09 1985-10-08 Thomas Industries, Inc. Multi-position relief valve
EP0255035A2 (fr) 1986-07-23 1988-02-03 Sanden Corporation Circuit frigorifique
US4932429A (en) * 1988-02-19 1990-06-12 Masatoshi Watanabe Screw stopper including anti-freeze device used for water pipe valve
US5161572A (en) * 1989-11-13 1992-11-10 Robert Bosch Gmbh Pressure valve
US5170638A (en) * 1990-02-01 1992-12-15 Carrier Corporation Variable area refrigerant expansion device
US5004008A (en) 1990-04-02 1991-04-02 Carrier Corporation Variable area refrigerant expansion device
US5139047A (en) * 1991-09-27 1992-08-18 Marotta Scientific Controls, Inc. Miniature check valve construction
US5332000A (en) * 1993-01-05 1994-07-26 Gassner, Inc. Low pressure sensitive valve

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7043937B2 (en) * 2004-02-23 2006-05-16 Carrier Corporation Fluid diode expansion device for heat pumps
US20050183439A1 (en) * 2004-02-23 2005-08-25 Alexander Lifson Fluid diode expansion device for heat pumps
US20180187788A1 (en) * 2008-03-27 2018-07-05 Water Management Solutions LLC Accuracy enhancing valve assembly and method
US20090289207A1 (en) * 2008-03-27 2009-11-26 Fabian Mauricio Barreda Airflow regulating valve assembly
US20100257916A1 (en) * 2008-03-27 2010-10-14 Ip Innovative Products, Llc Accuracy enhancing valve assembly and related method of use
US11555549B2 (en) * 2008-03-27 2023-01-17 Microflow, Llc, A Delaware Limited Liability Company Accuracy enhancing valve assembly and method
US10428963B2 (en) * 2008-03-27 2019-10-01 Water Management Solutions, Llc Accuracy enhancing valve assembly and method
US20100263397A1 (en) * 2009-04-16 2010-10-21 Fujikoki Corporation Motor-operated valve and refrigeration cycle using the same
US8763419B2 (en) * 2009-04-16 2014-07-01 Fujikoki Corporation Motor-operated valve and refrigeration cycle using the same
US20110154853A1 (en) * 2009-12-24 2011-06-30 Denso Corporation Decompression device
US8769984B2 (en) 2009-12-24 2014-07-08 Denso Corporation Decompression device
US8944098B1 (en) 2011-06-03 2015-02-03 Juan Carlos Bocos Airflow restricting valve assembly
CN105588380B (zh) * 2014-11-12 2018-04-06 株式会社鹭宫制作所 节流装置及具备该节流装置的冷冻循环系统
CN105588380A (zh) * 2014-11-12 2016-05-18 株式会社鹭宫制作所 节流装置及具备该节流装置的冷冻循环系统
US10222107B2 (en) 2015-06-03 2019-03-05 Saginomiya Seisakusho, Inc. Throttle device and refrigeration cycle system with same
US20180202567A1 (en) * 2015-09-04 2018-07-19 Saginomiya Seisakusho, Inc. Throttling device and refrigeration cycle
US10208867B2 (en) * 2015-09-04 2019-02-19 Saginomiya Seisakusho, Inc. Throttling device and refrigeration cycle
US10731904B2 (en) 2015-12-02 2020-08-04 Mitsubishi Electric Corporation Air conditioner
US20230034413A1 (en) * 2021-07-29 2023-02-02 Beaconmedaes Llc High flow check valve for medical gas applications

Also Published As

Publication number Publication date
DE69924798T2 (de) 2005-09-22
DE69924798D1 (de) 2005-05-25
JP3517369B2 (ja) 2004-04-12
EP0987505B1 (fr) 2005-04-20
EP0987505A2 (fr) 2000-03-22
ES2241218T3 (es) 2005-10-16
JP2000154952A (ja) 2000-06-06
EP0987505A3 (fr) 2001-12-05

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